Fuel injection apparatus



13 Sheets-Sheet l W m T T A INVENTOR- fl M. J. BERLYN FUEL INJECTION APPARATUS Jan. 13, 1953 Filed Aug. 7, 1948 MARTIN J. IBEELYN 1953 M. J. BERLYN 2,625,436

FUEL INJECTION APPARATUS Filed Aug. '7, 1948 15 Sheets-Sheet 2 34 INVENTOR. F1: 57. Z MAE'TIN J. BERLYN Jan. 13, 1953 M. J. BERLYN 2,625,436

FUEL INJECTION APPARATUS Filed Aug. T, 1948 13 Sheeqs-Sheet 5 .4 .[g 3. MA'ETIN J. BEELYN BY Xfi.

A TOP/VEY IN V EN TOR.

Jan. 13, 1953 M. J. BERLYN 2,625,436

FUEL INJECTION APPARATUS Filed Aug. '7, 1948 l3 Sheets-Sheet 4 34 INVENTOR. F 15. 4/ MARTIN J. IBEIZLYN Jan. 13, 1953 M. J. BERLYN FUEL INJECTION APPARATUS Filed Aug. 7, 1948 13 Sheets-Sheet 5 INVENTOR. PIAPTIN J. IBETZLYN ATTOPNY Jalii 1953 M. J. BERLYN 2,625,436

FUEL INJECTION APPARATUS Filed Aug. 7, 1948 13 Sheets-Sheet 6 34 INVENTOR. F1 9. 5.

MARTIN J. IBEELYN AT TOP/V5 5 Jan. 13, 1953 M, J, BERLYN FUEL INJECTION APPARATUS l3 Sheets-Sheet 9 Filed Aug. 7, 1948 R E mw W mm m m N Jan. 13, 1953 M. J. BERLYN 2,625,436

FUEL INJECTION APPARATUS Filed Aug. 7, 1948 13 Sheets-Sheet 1O INVENTOR. F '1 g. Z17. 34 MARTIN J. BEELYN AT TOPNL' Y Jan. 13, 1953 M. J. BERLYN FUELINJECTION APPARATUS l3 Sheets-Sheet 11 Filed Aug. '7, 1948 N A m mY N N L 2 mm m N B A J Jan. 13, 1953 M. J. BERLYN 2,625,436

FUEL. INJECTION APPARATUS Filed Aug. 7, 1948 l3 Sheets-Sheet 13 INVENTOR. MATZTIN J. BEE LYN F1 9.14 BY Patented Jan. 13, 1953 UNITED STATES PATENT OFFICE 9 Claims.

This invention relates to internal combustion engines, or the like, and has particular reference to new and improved fuel injection apparatus therefor.

An object of the invention is to provide a new and improved fuel injection apparatus for internal combustion engines, or the like, which apparatus is particularly adapted for use with crude fuels such as low quality liquid fuels and suspensions of finely pulverized solid fuels, such as coal, in liquid vehicles.

Another object of the invention is to provide a fuel injection apparatus which will achieve rapid injection and fine division of fuel particles with out recourse to high pressures.

Another object of the invention is to provide a fuel injection apparatus with which it is possible to achieve a constant pressure combustion cycle and thereby avoid the great cylinder pressures and combustion shock which create such structural and mechanical problems in conventional or contemporary high-output compressionignition engines working on the constant-volume cycle of combustion.

Another object of the invention is to provide fuel injection apparatu which takes up less space in critical regions of the cylinder head.

Another object of the invention is to provide fuel injection apparatus which avoids all of the mechanical complication and numerous operators previously required with conventional constructions to actuate the fuel valves and controls of engines employing blast-injection systems.

Another object of the invention is to provide a new and improved blast type fuel injection apparatus.

Another object of the invention is to provide a. new and improved blast type fuel injection apparatus and which may be operated using air or steam for the blast and which is particularly well adapted for use with steam and is not subject to trouble from condensation even when starting from cold.

Another object is to provide a fuel injection system of the blast type wherein exhaust heat from the engine may be used for generating blast steam when the engine is running.

Another object is to provide a blast type fuel injection system which, when employed with steam as a blast vapor, there may be achieved the smooth combustion of the air-blast engine without the disadvantage associated with the use of an air compressor.

' Another object is to provide a blast type fuel injection system wherein the amount of blast vapor per cycle is independent of engine speed, thus giving the system when applied to variable speed engines, a great advantage over previous blast injection systems.

Another object is to provide a new and improved fuel injection apparatus which may be employed with both compression ignition engines and spark ignition engines with the same advantages.

Another object is to provide a new and improved blast injection apparatus utilizing superheated steam.

Other objects and advantages of the invention will be apparent from the following description taken in connection with the accompanying drawings. Many changes may be made in the details of construction and arrangement of parts shown and described.

Referring to the drawings:

Fig. 1 is a fragmentary diagrammatic view of an engine embodying theinvention;

Fig. 2 is a diagrammatic view showing a fuel injection system constructed according to my invention at one point in its operation;

Figs. 3 to 6 inclusive are diagrammatic views of the system shown in Fig. 1 but showing the same at various points in its operation;

Figs. 7 to 10 inclusive are diagrammatic views generally similar to Figs. 2 to 6 inclusive, but illustrating the consequences of failure of various elements of the injection system;

Fig. 11 is a top or plan view of the preferred embodiment of my invention;

Fig. 12 is a sectional view taken on line lZ-IZ of Fig. 11, looking in the direction of the arrows;

Fig. 13 is a sectional view taken on line l3-I3 of Fig. 11, looking in the direction of the arrows;

Fig. 14 is a sectional view taken on line I4-|4 of Fig. 11, looking in the direction of the arrows;

Fig. 15 is a sectional view taken on line [5-45 of Fig. 11, looking in the direction of the arrows; and

Fig. 16 isa sectional view taken on line l6-|6 of Fig. 14, looking in the direction of the arrows.

Referring more particularly to the drawings wherein similar reference characters designate corresponding parts throughout the several views, Fig. l is a diagrammatic view showing, by way of example, the application of the present invention to one cylinder of a four-stroke cycle engine. While the application shown is to but a single cylinder of a four-stroke cycle engine, the system is equally applicable to multi-cylinder engines as hereinafter set forth and is also equally appli cable to two-stroke cycle engines.

In the arrangement shown in Fig. 1, l is the air-intake pipe and la the air filter of a conventional four-stroke cycle compression-ignition engine; 2 is the exhaust pipe; 3 is a conventional flash-steam boiler utilizing the exhaust heat from the engine through exhaust pipe 2 to generate high pressure superheated steam and deliver the same through pipes 3a and 3b to injector I4. A temperature-sensitive element 4 cooperates with the bellows or similar device 5 which actuates the control of fuel burner 6 in response to the temperature of the steam leaving flash boiler 3. A boiler feed pump 1 draws water from water tank 8 and pipe line 8a and delivers it under pressure through pipe line 8?) to flash boiler '3. A surgedamper 9, of conventional type, is provided in the boiler feed pipe line 812. I I

Water pump '1' is actuated by a cam la on the engine camshaft l and is controlledby means of a pressure-responsive device H so that falling steam pressure causes pump T to deliver feedwater to flash boiler 3 at a greater rate. The pressure-responsive device H is connected-by pipe line Ha to the outlet from the flash boiler, such as pipe 30. or pipe 31). The pressure-responsive device It is adapted to adjust pump control rack lb to which said pressure-responsive device is connected to automatically adjust the supply of water from supply tank 8 to flash boiler 3, at a greater rate as previously described.

Fuel supply, tank I2 is connected by pipe lines Hz and 217 to burner 6 and by said pipe line 12a to a conventional type fuel injection pump and governor 13 which is adapted to deliver fuel through line lSa to injector M, the construction and operation of which is hereinafter described. Pipe Ma is a fuel return or bypass pipe as hereinafter described.

I is a reservoir of compressed air which is connected by a pipe 15a withburner 6 and I6 is a conventional electric igniter plug that may be energized by a conventional spark coil or ignition transformer.

The engine is provided with the usual combustion chamber or cylinder l1 into which projects injector M and in which is mounted the piston 18 which is connected by connecting rod ill to crankshaft 20. Inlet valve 21 and exhaust valve 22 are adapted to be actuated by rocker levers 23 and 24 respectively and which are both actuated by cams on camshaft 10.

The injector or injection system l4 and various steps in its operation is shown diagrammatically in Figs. 2 to inclusive and the preferred form is shown in Figs. 11 to 16 inclusive. This injector or fuel injection system comprises four main functional units, namely, the injection valve, with which is associated the nozzle, and which is designated generally at A, a steam accumulator designated generally at B, a shuttle valve designated generally at C and a fuel accumulator designated generally at D.

The injection valve A consists of the valve housing 25 which contains the differential valve 26 which is provided with a guide portion 27, of greater diameter than valve face extension 28, and which is also provided on its opposite end with the travel limiting boss 29. H

Nozzle 36 is aligned with valve housing 25 and has the seat 3! adapted to be engaged by valve face 32 of valve 26, to control flow through nozzle 36 which is also provided with internal grooves 33 tqpromote turbulence of flow and orifices 34 of desired number and sizeto, direct the.. spray 4 of fuel into the combustion chamber of the engine.

Steam accumulator B consists of a housing 35 and communicates with injection valve housing 25 through duct 36 and also communicates with housing 31 and shuttle valve C through duct 38 and port 39.

In shuttle-valve housing 3'! is positioned shuttle valve 40, which is free to move axially in said shuttle-valve housing 37. Theshuttle valve 40 is provided with two cylindrical lands ii and 42 and a mushroom-type valve head 43. The lands 4i and 42 are a sliding fit in bore :14 of housing 3i and the valve head 43 is a sliding fit in counby abutting on seat 46 at the adjacent ends of .bore 44 and counterbore 45. Shuttle-valve housing 31 is also provided with another counterbore 67 which is larger in diameter than counterbore45.

Shuttle valve mushroom head 43 is proyided with a boss 48 which limits travel in one direction by abutting against the closure 49 of housing3'l. Housing 3'1 is provided with ports 39, 50, 5|, 52, 53 and 54. Port 39 isalways open and communicates by way of duct 38, with steam accumulator 35. Port 55, which maybe closed by land 42 of shuttle valve 40, communicates by way of duct 55 with port 56 of injection valve housing 25. Port 5i, which is always open, communicates by way of duct 51 with port 58 of injection valve housing 25. Port 52, which is always open, communicates by way of duct 1311 with a conventional diesel injection pump '13 of the type which allows some reversal of fuel flow through its discharge port at the end of each injection.

Port .53 is controlled by land 52 of shuttlevalve 46, and it may be opened by either edge of the land 42 or it may be closed by the land 42 and said port 53 communicates by way of duct 59 with port 60of the fuel accumulator housing .6l.which is provided with an axially movable free piston 62 having motion-limiting bosses 63 and 64 on its opposite ends which abut against the closures '65 and 65 respectively of housing 6| at the limits of axial travel of piston 62.

Fuel accumulator housing Si is provided with ports 60, 61, 68 and 69. Duct port 61, which communicates with overflow duct la is normally closed by piston 62 but maybe uncovered by the piston 62 when it has travelled almost to the limit of its movement in the direction limited by abutment boss 64 against closure 66 thus allowing communication of duct 59 with duct Ma. Port 68, which is always open, is in communication with a sourcev of high-pressure steam by way of duct l0.v Port 69 is normally openbut may be closed by piston 62 as it travels towards the closure 66. Ports 6! and 69 are so located and the length of piston 62 is such that port 69 is closed before port 67 is opened. Port 69 communicates with port 54 of shuttle-valve housing 3! by way of duct H. A relatively small duct 12, forming a constricted passage for steam, constantly conne'cts ducts 10 and H at a point in duct H between ports 69 and 54.

Referring to Figs. 2, 3, 4, 5 and 6, the construction and functioning or operation or the system may be understood.

Fig.2 shows valves 26 and, 40 and piston 62 in thepositions they assume at the end of an injection during regular cyclical Operation on a running engine. Steam pressure from accumulator 35, by way of duct 36 and port 36a,'has forced injection valve 26 to the limit of travel permitted byabutment of boss 29 against the closure or abutment of housing 25, and valve-face 32 on valve extension 28 is clear of seating 3|. Steam pressure has forced mushroom head 43 of valve 40 into'contact with seat 46. Steam pressure has forced piston 62 to the limit of travel permitted by abutment of boss 63 against closure 65'and fuel has been pumped by Way of ports 60,- duct 59, bore 44, port 56, duct 55 and port 56 to nozzle 25a.- Displacement of fuel by guide portion 2'! of injection valve 26, also by land 42 of shuttle-valve 46, has been accommodated by backfiow along duct |3a as permitted by the fuel pump atthe end of its delivery phase. a I

Fig. 3 shows valves 26 and 46 and piston 62 in the positions they assume when the fuel pump has commenced delivery of the next charge of fuel. Injection valve 26 has been forced by fuel pressure, communicated to guide portion 21 through duct l3a, port 52, bore 44, port 5|,-duct 51 and port 58, to the limit of travel resulting from abutment of valve-face 32 of valve extension 28 against seating 3|. In this position of the injection valve 26 the port 56 is closed by guide-portion 21. Shuttle valve 40 is being forced by fuel pressure, communicated to land 42 through duct |3a and port 52, in the direction which unseats the mushroom head 43 from the seating 46. Fuel pressure must be greater than steam pressure since the area'of the mushoom head 43 is greater than bore 44 in which land 42 is sliding. Piston 62 is still held by steam pressure in the position as in Fig. 2.

Fig. 4 shows valves 26 and 49 and piston 62 in the positions they assume later in the'delivery stroke of the fuel pump. Injection valve 26 is still forced into the position shown in Fig. 3. Shuttle valve 46 has been forced to the limit of travel as permitted by abutment of boss 48 against closur 49. The mushroom head 43 is now clear of counterbore 45 and high pressure steam is admitted to steam accumulator 35 by way of duct 76, ports 68 and 69, duct 1|, port 54, counterbores 41 and 45, bore 44, port 39 and duct 38. With the shuttle valve 40 in this position, land 42 has passed port 53 and fuel has been forced into the fuel accumulator by way of duct |3a, port 52, bore 44, port 53, duct 59 and port 66. Piston 62 has been forced by fuel pressure, in excess of steam pressure, to move'in the direction remote from closure 65. The distance travelled in this direction by the fuel accumulator piston 62 is determined by the volume of fuel delivered per stroke by the fuel pump. This is the situation just prior to the beginning of an injection through nozzle 25a.

Fig. 5 shows valves 26 and 46 and piston 62 in the transient positions they assume during the initial stages of an injection, the fuel pump having completed its fuel delivery phase and having unloaded the duct |3a of pressure and left the way open for a reversal of fuel flow direction through this duct. Steam pressure acting on the differential area of the valve-face end of valve 26 causes the unseating of this valve from seat 3| since opposing fuel pressure acting on the opposite end of guide-portion 21 has been removed by. the duct-unloadin action of the fuel pump. Steam begins to issue from the nozzle 25a. Port 56 has been uncovered but no fuel issues therefrom as yet because land 42 of shuttle valve 40 hasnot yet uncovered port 53,-but valve is moving rapidly in the direction towards abutment of the mushroom head on seat 46 being forced-by steam pressure on the large area of the mushroom head andhaving little opposing fuel pressure on land 42 to resist this motion.

i Fig. 6 shows valves 26 and 40 and piston 62 in the positions they assume during the midpoint of injection. Injection valve 26 has moved to the limit prescribed by abutment of boss 29 against the closur or abutment of housing 25 and port 56 is fully uncovered. Shuttle valve 40 has moved to the limit of travel when mushroom head 43 has seated on seat 46 and in this position port 53 has been fully uncovered by land 42. Piston 62 is being forced axially by steam pressure towards the limit where boss 63 abuts closure 65 and fuel is being pumped by piston 62 through port 69, duct 59, port 53, bore 44, port 56; duct 55, port 56 past seat 3|, through nozzle 25a and out of orifices 34. At the same time steam which was accumulated in steam accumulator 35 is flowing through duct 36 and port 36a past seat 3| and-mixing, under a state of high turbulence, in grooves 33, with the fuel and issues with the fuel through orifices 34. 'When piston 62 reaches the limit of its travel as shown in Fig. 2, injection is ended and the whole cycle repeats. All these moving parts of the injector assembly, injector valve 26, shuttle valve 40 and fuel accumulator piston 62, are normally thrustinone direction bysteam pressure in excess of fuel pressure and in the other directionby fuel pressure in excess of steam pressure. Since the fuel injection pump is capable of delivering pressures greatly in excess of the maximum steam pressure, a seized element will cease movement when substantially at the limit of its travel in the direction in which it is thrust by excess of fuel pressure over steam pressure.

Fig. '7 illustrates the consequences of seizure of injector valve 26. The valve will eventually jam in the position where extension 28 is in contact, or nearly in contact, with seat 3|; port 56 will be closed off by guide portion 21 of the valve and fuel will not be able to follow its prescribed normal path along ducts 59 and 55, and fuel accumulator piston 62 will not make a fuel delivery stroke; Successive charges of fuel entering duct l3a'from the fuel injection pump will move piston 62 to that end of its travel where boss 64 makes, or nearly makes, contact with'closure 66; further charges of fuel entering duct |3a will be re jected by way of duct |4a without giving rise to excessive stresses in the structure of the injector itself or of the fuel injection pump. Piston 62 will reciprocate slightly in response to incoming charges of fuel but will not move in, in the direction due to steam pressure thrust, appreciably past the point where overflow port 61 is closed off; furthermore, during the Whole of this "restricted reciprocation of piston 62, port 69 will remain closed and steam can only reach the steam accumulator 35 and, if valve 26 is not completely seated, the nozzle 25a by way of the constricted passage 12. Shuttle valve 40 will continue to reciprocate but fuel will only now in one direction, towards the fuel accumulator, through port 53 and there will be no flow through ports 50 or 5|. With a seized injector valve. therefore, there will be no fuel passing through the nozzle, and only as much steam will escape as can pass through restricted passage 12. V

Fig. 8 illustrates the result of a seized shuttle valve 46. which will cease mcvementwhen in a {position in which boss 43 -zle 2 5a..

sponse to successive fuel charges, will reciprocate with limited amplitude substantially as in the case of a seized injector valve shown in Fig. 7. Steam has access to steam accumulator 35 and nozzle 250. only by way of the restricted passage I2. Injector valve iii will reciprocate throughout its normal range of motion and some steam will issue from the nozzle 25a in each cycle,

but no fuel will be discharged through the nozzle 25a, because port 50 is closed by land 42 ofshuttle valve 40. There will be slightly greater amplitude of reciprocationof piston 62 than in the previous case owing to the active displacement of guide portion 21' of injector valve 26.- r

Fig. 9 shows seizure of fuel accumulator piston 62 which will come to rest with boss 64 touching, or nearly touching, closure 86. Port 61 will be partially or fully open and port '69 will be closed. Shuttle valve 40 and injector valve 26 willreciprocate throughout their normal operating ranges of motion. Since piston 52 does not make a delivery stroke, no fuel will issue from nozzle 25a and the only steam which can pass through the nozzle is that which finds its way through constricted passage 12. Charges of fuel entering duct l3a from the fuel injection pump will escape by way of overflow port 61 without giving rise to abnormalstresses in the injector structure or the fuel injection pump or its operating mechanisms.

'Fig. 10 represents the case where there is no steam supply to an injector assembly but the engine is turning and the fuel injection pump is delivering charges of fuel in the normal manner. Such a condition might arise out of an attempt to start the engine without first providing a head of steam from the flash boiler, or the water supply to the boiler feed pump might fail while the engine is running; in any event it is undesirable to flood the engine cylinders with fuel which has not been injected in the form of a spray since fuel so introduced will not burn properly and may foul the engine.

When there is no steam pressurein duct l0, fuel entering duct 13a. will thrust shuttle valve 40 to the limit of its travel at which boss 18 abuts closure 49 and injector valve 25a will move to the limit of travel where it seats on seat 3|. Fuel accumulator piston 82 will move to the limit where boss 64 makes contact with closure 65 and no further movements of these three components will take place until steam pressure is established in duct 10.

All fuel entering duct [30, will pass out of the injector assembly through overflow port 61. Establishment of steam pressure in duct 10 will give rise to steam flow through restricted duct '12 and this will cause the shuttle valve to move to the other end of its travel between delivery strokes of the fuel injection pump, when, fuel pressure in duct [3a is relieved, and fuel accumulator piston 62 will be enabled to force fuel, by way of ducts 59 and 55 to nozzle 25a; port 69 will then be uncovered; port 61 will be closed and normal functioning of the system will be reestablished.

The purpose of duct 72 is to permit this rees-v tablishment of normal functioning if, for any cause, the moving parts of the injector assembly should come to rest in the combination of positions as shown in Fig. 10-which would happen if any engine operator shut the steam supply off before stopping the engine; it might also occur if the engine were left standing without operation for a period of time with some residual pressure, such as gravity head, of fuel in duct l3a.

t In Figs. 11 to 16 inclusive there is shown the preferred form of execution of the invention, which form is believed to be relatively simple and economical in construction and efficient in operation.

In this form of invention the parts thereof corresponding to those shown in the diagrammatic drawings have been correspondingly numbered so far as practicable for convenience in referring to those views of the drawings. H 3

In the preferred form there is provided -a tapered housing I3 having an opening and adapted to be closed by the cap or cover 14 which is retained in position on the housing 73 by means of the screws 75 and said cap or cover 14 is adapted to be sealed by the gasket 16.

Within the housing 1'3 is positioned a member H which has its outersurface formed so as to correspond with the inner surface of the housing 13 and so as to closely engage the same when the member H is placed within said housing.

The member 11 has the threaded extension 18 to which is connected the nozzle 25a adapted to receive fuel through the duct 9 and having a turbulence promoting arrangement corresponding to that numbered 33 in the diagrammatic drawings and which arrangement is formed by the alternate washers 82! which have alternating sized central apertures 8| and 82 as shown.

The member H has a central bore beginning with the bore (9, previously described, and progressively increasing in cross section from said bore 19 to the opposite end of said member 11 which arrangement facilitates the manufacturing and assemblyof the device.

In this form of the invention the ducts for fuel and steam are preferably formed in the outer surface of the member H as shown although they could be formed on the inner surface of the casing 13 if desiredand said ducts are provided with the necessary ports for communicating with the central bore or aperture.

In this form of the invention the fuel accumulator valve 62 works in the opposite direction to that shown in the diagrammatic drawings and as will be seen, the closures 65 and 66 are on the reverse sides of said accumulator piston 62 from that shown in the diagrammatic drawings such as ri In this form of the invention the steam accumulator 35 is positioned adjacent the upper end, of .thecasing I3.

The closure member 65 is provided with the reduced extension 83 which fits within the opening in the member 84 and is locked in position by the socket head set screws 85 and 86 which are threaded into the opening in the member 84 and the whole assembly is retained in operative position within the casing 13 by means of the spring ring 87 which is inserted into a slot 83 in the inner periphery of the housing 13 and engages the upper. surfaces of the member 84.

In this form of the invention, as will be seen from Fig. 12, the constricted opening 72 is formed by forming the disc closure 49 with the constricted opening 12 and locking said closure 49 in position by means of the threaded closuremember .66 which; has a plurality of openings therein adapted to communicate with said constricted opening 12.

The transverse slot 89 is provided in the member 11 between the valve 26 and the shuttle valve 40 and in this slot is positioned the member 90 which is in the form of a narrow abutment having openings on the opposite sides thereof and which abutment serves to act as a stop for the valve 21 but allows communication with the shuttle valve 40 in the manner similar to the port 58 and duct 51 as shown in the diagrammatic views.

It is pointed out that by employing the tapered housing 13 with the tapered insert or member 11 .and also by the use of the central bore or orifice having areas progressivelyincreasin in size from the bore 19 to the opposite end of the member 11, that the manufacture of the members with the precision required for properly constricting the same is greatly facilitated. V

In operation of the engine using this injection system, a normal governor causes fuel'injection 13 to deliver fuel to injector I4 in accordance with the requirements of the engine and steam is supplied to the injector M by flash boiler 3. Should the engine exhaust not provide'suflicient heat to maintain the desired steam temperature, the temperature-sensitive element 4 will cause bellows 5 to move the control lever of burner 6 in a direction to feed a spray of fuel and air into the flash boiler 3 and at the same time igniterplug IE will be energized so as to light the burner in the event that the exhaust heat in the system is insufficient to promote ignition. Should the steam pressure fall below the prescribed minimum, the spring in pressure-responsive element II will overcome the piston force and will cause the control rod of boiler feed pump 1 to move in a direction to increase the rate of water feed to flash boiler 3.

Burner 6 and igniter plug l6 are also used for the purpose of generating the necessary head of steam for injection when starting the engine, at which time no exhaust heat is available. When the running engine provides adequate exhaust heat for generation of steam at the required pressure and temperature, element 4 in cooperation saryto secure the same result with presently employed apparatus. The pumping of liquids containing suspended solid particles has previously resulted in serious erosion of the fuel injection equipment if the pressures are high such as 5000 lbs. p. s. i. and higher, whereas with pressures of 3000 lbs. p. s. i. or lower the abrasive effect of the solid particles is inconsiderable. The pressures contemplated with the present invention are a maximum of 1500 lbs. p. s. i.

One typical example of pressures which may be employed are, steam pressure of 1000 lbs. 1). s. i., fuel peak pressure approximately 1200 lbs. p. s. i., maximum combustion pressure in the engine approximately 800 lbs. p. s. i.

The method and apparatus of the present invention maybe employed with compression ignition engines and spark ignition engines with the same advantages.

superheated steam is employed in order that, where a liquid fuel is employed, the fuel will be evaporated by the superheatedsteam as it enters the combustion chamber o'fgthe engine, and where a suspension of solid fuel particles in a liquid vehicle is employed, the superheated steam will evaporate the liquid vehicle so that the solid particles of fuel may be in a dry state when introduced to the air in the engine combustion chamber. Also, the use of steam tends to reduce ignition lag.

From-the foregoing it will be seen that I have provided simple, efi'lcientand economical means for obtaining all of the objects and advantages of accumulator connected to said source of vapor and to said injection valve by passageways for supplying vapor to said injection'valve, 'a' fuel passageway connecting said fuel accumulator and said injection valve and a shuttle valve connected to said fuel passageway-intermediate said fuel accumulator and said injection valve and also with said vaporpassageway intermediate said source of vapor and said vapor-accumulator, said shuttle valve having opposed pressure responsive surfaces adapted to be acted upon by vapor and fuel respectively, said shuttle valve being actuated by coordinated changing pressure conditions in the fuel and vapor on the respective pressure'responsive surfaces of said shuttle valve to control the delivery of fuel-to said injection valve and vapor to said vapor accumulator, and said injection valve having avalve member having opposed pressure responsive surfaces adapted to be acted upon by vapor and fuel respectively. p

2. In a device of the character described, a fuel accumulator-having an inlet passage for connection to a source of fuel and a passage for connection to a source of vapor, a piston in said fuel accumulator, said piston having opposed pressure responsive surfaces, one of saidsurfaces being acted upon by vapor and the other of said surfaces being acted upon by fuel, an injection valve, a 'vapor accumulator connected to said source of vapor and to said injection valve by passageways for supplying vapor to said injection valve, a fuel passageway connecting said fuel accumulator and said injection valve and a shuttle valve connected to said fuel passageway intermediate said fuel accumulator and said injection valve and also with vapor passageway intermediatesaid source of vapor and said vapor accumulator, said shuttle valve having opposed pressure responsive surfaces, one of said surfaces being acted upon by vapor and the other of said surfaces being acted upon by fuel, said shuttle valve being actuated by coordinated changing pressure conditions in the fuel and vapor on the respective pressure responsive surfaces of said shuttle valve to control the delivery of fuel to said injection valve and vapor tosaid'vapor accumulator, said injection valve having a valve member having opposed pressure responsive surfaces, one of said surfaces being acted upon by vapor and the other of said surfaces being acted upon by fuel.

3. In a device of the character described, a fuel accumulator having an inlet passage for connection to a source of fuel and a passage for connection to a source of vapor, a piston in said fuel accumulator and having opposed pressure responsive surfaces to be acted upon by vapor and fuel pressure respectively, an injection valve, a vapor accumulator connected to said source of vapor and to said injection valve by passageways for supplying vapor to said injection valve, a fuel passageway connecting said fuel accumulator and said injection valve and a shuttle valve connected to said fuel passageway intermediate said fuel accumulator and said injection valve and also with said vapor passageway intermediate said source of vapor and said vapor accumulator, said shuttle valve having opposed pressure responsive surfaces to be acted upon by vapor and fuel respectively, said shuttle valve being actuated by coordinated changing pressureconditions in the fuel and vapor on the respective pressure respon sive surfaces of said shuttle valve to control the delivery of fuel to said injection valve and vapor to said vapor accumulator, and said injection valve having a valve member having. opposed pressure responsive surfaces to be acted upon by vapor and fuel respectively and a fuel passage for supplying fuel to said injection valve for delivery to a combustion chamber,

4. In a device of the character described, a fuel accumulator having an inlet passage for connection to a source of fuel and a passage for connection to a source of vapor, a piston in said fuel accumulator and having opposed pressure responsive surfaces to be acted upon by vapor and fuel pressure respectively, an injection, valve, a vapor accumulator connected to said source of vapor and to said injection valve by passageways for supplying vapor to said injection valve, a fuel passageway connecting said fuel accumulator and said injection valve and a shuttle valve connected to said fuel passageway intermediate said fuel accumulator and said injection valve and also with said vapor passageway intermediate said source of vapor and saidvapor accumulator, said shuttle valve having opposed pressure responsive surfaces to be acted upon by vapor and fuel respectively, said shuttle valve being actuated by coordinated changing pressure conditions in the fuel and vapor on the respective pressure responsivesurfaces of said shuttle valve to control the delivery of fuel to said injection valve and vapor to said vapor accumulator, and said injection valve having ;a valve member having opposed pressure responsive surfaces to. be acted upon by vapor and fuel respectively, said injection valve being adapted to be opened by vapor pressure acting uponone of said surfaces and a fuel passage ,for supplyingfuel to, said injection valve for delivery to a combustion chamber when said injection valve is opened.

5.,In a device of the character described, a fuel accumulator having an inlet passage. for con nection to a source of fuel and a passage for connection to a sourceof vapor, a piston in said fuel accumulator, said piston having opposed pressureresponsive surfaces, one of said surfaces being acted upon by vapor and the other of said surfaces beingacted upon by fuel, aninjection valve, a .vapor accumulator connected to said source of vapor and to said injection valve by passageways for supplying vapor to said. injection valve, a fuel passageway connecting said fuel accumulator and said injection valve and a shuttle valve connected to said fuel passageway intermediate said fuel accumulator and said injection valve and also with said vapor passageway intermediate said source of vapor and said vapor accumulator, said shuttle valve having opposed pressure responsive surfaces, one of said 112 surfaces being adapted'to be acted upon byvapor and the other of said surfaces being "adapted to be acted upon by fuel, said shuttle valve being actuated by coordinated changing pressure condi tions in the fuel and vapor on the respective pressure responsive surfaces of said shuttle valve to control the delivery of fuel to said injection valve and vapor to said vapor accumulator, said injection valve having a valve member having opposed pressure responsive surfaces, one of said surfaces being acted upon by vapor and the other of said surfaces being acted upon by fuel, and a fuel passageway for supplying fuel to said injection valve for delivery to a combustion chamber.

6. In a device. of the character described, a fuel accumulator having a passage for connection to a source of fuel and a passage for connection to a source of vapor, a piston in said fuel accumulator, said piston having opposed pressure responsive surfaces, one of said surfaces being acted upon by vapor and the other of said surfaces being acted upon by fuel, an injection valve, a vapor accumulator connected to said source of vapor and to said injection valve by passageways for supplying vapor to said injection valve,'a fuel passageway connecting said fuel accumulator and said injection valve and a shuttle valve connected to said fuelpassageway intermediate said fuel accumulator and said injection valve and also with said vapor passageway intermediate said source of vapor and said vapor accumulator, said shuttle valve having opposed pressure responsive surfaces, one of said surfaces being acted upon byvapor and the other of said surfaces being acted'upon by fuel, said shuttle valve being actuated by coordinated changing pressure conditions in the fuel and vapor on the respective pressure responsive surfaces of said shuttle valve to control the delivery of fuel to said injection valve and vapor to said vapor accumulator, said injection valve having a valve member having opposed pressure responsive surfaces, one of said surfaces being acted upon by vapor and the other of said surfaces being acted upon by fuel, said injection valve being opened by vapor pressure acting upon one of said surfaces and a fuel passage for supplying fuel to'said injection valve for delivery to a combustion chamber when said injection valve is opened.

7. In a device of'the character described, a fuel accumulator having a passage for connection to a source of fuel and a passage for connection to a source of vapor, a piston in said fuel accumulator, said piston having opposed pressure responsive surfaces, one of said'surfaces being acted upon by vapor and the other of said surfaces being acted upon by fuel, aninjection valve, a vapor accumulator connected to said source of vapor through said fuel accumulator and tosaid injection valve by passageways for supplying vapor to said injection valve, a fuel passageway connecting said fuel accumulator and said injection valve and a shuttle valve connected to said fuel passageway intermediate said fuel accumulator and said injection valve and also with said vapor passageway intermediate said source of vapor and said vapor accumulator, said shuttle valve having opposed pressure responsive surfaces, one of said surfaces being acted upon by vapor and the other of said surfaces being acted upon by fuel, said shuttle valve being actuated by coordinated changing pressure conditions in the fuel and vapor on the respective pressure responsive surfaces of said shuttle valve to control the delivery of fuel to said injection valve and vapor to said vapor accumulator, said injection valve having a valve member having opposed pressure responsive surfaces, one of said surfaces being acted upon by vapor and the other of said surfaces being acted upon by fuel.

8. In a device of the character described, a fuel accumulator having a passage for connection to a source of fuel and a passage for connection to a source of vapor, a pistonin said fuel accumulator and having opposed pressure responsive surfaces to be acted upon by vapor and fuel pressure respectively, an injection valve, a vapor accumulator connected to said source of vapor and to said injection valve by passageways for supplying vapor to said injection valve, a fuel passageway connecting said fuel accumulator and said injection valve and a shuttle valveconnected to said fuel passageway intermediate said fuel accumulator and said injection valve and also with said vapor passageway intermediate said source of vapor and said vapor accumulator, said shuttle valve having opposed pressure responsive surfaces to be acted upon by vapor and fuel respectively and said injection valve having a valve member having opposed pressure responsive surfaces to be acted upon by vapor and fuel respectively, said injection valve being opened by vapor pressure acting upon one of said surfaces by vapor from said vapor accumulator, said shuttle valve being actuated by coordinated changing pressure conditions in the fuel and vapor on the respective pressure responsive surfaces of said shuttle valve to control the delivery of fuel to said injection valve and vapor to said vapor accumulator, said injection valve allowing the injection of vapor upon such opening of said injection valve and a fuel passage to be opened upon further opening of said injection valve to allow the injection of fuel.

9. In a device of the character described, a fuel accumulator having a passage for connection to a source of fuel and a passage for connection to a source of vapor, a piston in said fuel accumulator, said piston having opposed pressure responsive surfaces, one of said surfaces being acted upon by vapor and the other of said surfaces being acted upon by fuel, an injection valve, a vapor accumulator connected to said source of vapor and to said injection valve by passageways for supplying vapor to said injection valve, a fuel passageway connecting said fuel accumulator and said injection valve and a shuttle valve connected to said fuel passageway intermediate said fuel accumulator and said injection valve and also with said vapor passageway intermediate said source of vapor and said vapor accumulator, said shuttle valve having opposed pressure responsive surfaces, one of said surfaces being acted upon by vapor and the other of said surfaces being acted upon by fuel, said injection valve having a valve member having opposed pressure responsive surfaces, one of said surfaces being acted upon by vapor and the other of said surfaces being acted upon by fuel, said shuttle valve being actuated by coordinated changing pressure conditions in the fuel and vapor on the respective pressure responsive surfaces of said shuttle valve to control the delivery of fuel to said injection valve and vapor to said vapor accumulator, said injection valve being opened by vapor pressure acting upon one of said surfaces by vapor from said vapor accumulator, said injection valve allowing the injection of vapor upon such opening of said injection valve and a fuel passage to be opened upon further opening of said injection valve to allow the injection of fuel.

MARTIN J. BERLYN.

REFERENCES CITED The following references are of record in the file of this patent:

UNITED STATES PATENTS Number Name Date 1,164,064 Brown Dec. 14, 1915 1,363,470 Knudsen Dec. 28, 1920 1,445,828 Fesler Feb. 20, 1923 1,586,006 Rochefort May 25, 1926 1,976,528 Vandeveer Oct. 9, 1934 2,319,591 Ferguson May 18, 1943 FOREIGN PATENTS Number Country Date 736,661 France Sept. 20, 1932 

